Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/1207—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by the supporting arrangement of the damper unit
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/1203—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by manufacturing, e.g. assembling or testing procedures for the damper units
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
  • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
  • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F2230/00—Purpose; Design features
  • F16F2230/32—Modular design
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
  • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers

Definitions

• the invention relates to a torque transmission device according to claim 1 and 4
• a power transmission device for power transmission between a prime mover and an output is known, wherein the power transmission device comprises a series damper.
• an improved torque transmitting device can be provided by rotatably supporting the torque transmitting device about an axis of rotation and comprising a series damper having a first damper unit, a second damper unit and a coupling unit, the first damper unit having a damper output side and the second damper unit being a damper input side wherein the coupling unit between the damper output side and the damper input side is arranged, wherein the coupling unit comprises a first coupling part and a second coupling part, wherein the first coupling part and the second coupling part are axially offset from each other, wherein the first coupling part the damper output side with the second Coupling part connects, wherein the second coupling part connects the first coupling part with the damper input side.
• the torque transmission device can be constructed modularly, so that depending on the requirement profile of the torque transmission device, a part of the components of the torque transmission device can be changed without the other components can be adapted in their structural design to the changed components.
• the adaptation is made by the two-part coupling unit.
• the torque transmission device has an output shaft, wherein the coupling unit has a connection hub, wherein the connection hub is rotatably mounted on the output shaft, wherein the connection hub has an external toothing on the circumference, wherein the first coupling part has an internal toothing and the second coupling part has a further internal toothing , wherein the internal toothing and the further internal toothing engage in the external toothing.
• the coupling parts can be inserted in the axial direction in the assembly of the torque transmission device, so that an assembly time is particularly low and the assembly can be automated.
• the torque transmission device has a tensioning means, wherein the tensioning means, between a first component and a second component, preferably between the first coupling part and the second coupling part, is arranged, wherein the tensioning means is formed, the first component against the second components , Preferably to clamp the first coupling part against the second coupling part, preferably in the axial direction and / or in the circumferential direction.
• an improved torque transmitting device can be provided in that the torque transmission device is rotatably mountable about an axis of rotation, wherein the torque transmitting device tion a turbine wheel of a hydrodynamic converter and a series damper having a first damper unit, a second damper unit and a coupling unit, wherein the coupling unit torque-locking the first damper unit connects to the second damper unit, wherein the turbine wheel is torque-locking connected to the coupling unit.
• the torque transmission device has at least one speed-adaptive absorber, in particular a centrifugal pendulum, wherein the speed-adaptive absorber has at least one Tilgerflansch, the Tilgerflansch with the coupling unit torque-locking, preferably positive and / or non-positively connected, or in one piece and the same material with the Coupling unit is formed.
• the Tilgerflansch an internal toothing, wherein the Tilgerflansch is disposed axially between the first coupling part and the second coupling part, wherein the internal toothing engages in the outer toothing and the Tilgerflansch torque-locking manner with the connecting hub.
• the speed-adaptive damper is arranged radially between the first damper unit and the second damper unit, and / or wherein preferably the first damper unit, the second damper unit and the speed-adaptive damper are arranged axially overlapping.
• the torque transmission device can be made particularly compact.
• the first damper unit has a first one
• the coupling unit has a further coupling part, wherein the further coupling part is connected on one side to the turbine wheel and is connected on the other side to the first coupling part and / or the second coupling part, wherein preferably the further coupling part means a positive connection, in particular a pluggable connection in the axial direction, is connected to the first coupling part and / or the second coupling part.
• the torque transmission device has a further speed-adaptive absorber with a Tilgerflansch, wherein the further coupling part extends substantially in the axial direction, wherein the further Tilgerflansch extends substantially in the radial direction and radially on the inside or radially outside with the other Coupling member is connected by means of a pluggable connection in the axial direction.
• Figure 1 is a schematic representation of a torque transmitting device according to a first embodiment.
• FIGS. 3-23 are each a semi-longitudinal section through a torque transmission device according to a second to twenty-second embodiment.
• FIG. 1 shows a schematic illustration of a torque transmission device 10 according to a first embodiment.
• the torque transmission device 10 has an input side 20 and an output side 25.
• the input side 20 may, for example, be connected in a torque-locking manner to a drive motor of a drive train of a motor vehicle.
• the output side 25 may, for example, be connected in a torque-locking manner to a transmission device 30, in particular to a vehicle transmission of the motor vehicle.
• the output side 25 may be connected torque-tight with another component of the drive train.
• input side 20 and output side 25 can be reversed.
• the torque transmission device 10 further includes a hydrodynamic converter 35, a lock-up clutch 40, a series damper 45 and a first to fourth speed-adaptive damper 50, 55, 60, 65.
• the speed-adaptive absorber 50, 55, 60, 65 is exemplified as a centrifugal pendulum. Also, the speed-adaptive absorber 50, 55, 60, 65 may be formed differently. In particular, it is conceivable that the speed-adaptive absorber 50, 55, 60, 65 as trapezoidal centrifugal pendulum or Parallelfliehkraftpendel with one or more absorber masses 220, 235, 245, 255, 325, which are arranged inside or outside, is formed.
• the number of the speed-adaptive absorbers 50, 55, 60, 65 in the embodiment is exemplary. Of course, a different number of speed-adaptive Tilgern 50, 55, 60, 65 may be provided.
• the series damper 45 has at least a first damper unit 70, a second damper unit 75 and a coupling unit 80.
• the first damper unit 70 has a first damper element 85 and the second damper unit 75 has a second damper element 90.
• the damper element 85, 90 may be an arrangement of one or more springs, in particular compression springs, tension springs and / or bow springs. Also, another embodiment of the damper element 85, 90 is conceivable.
• the first damper unit 70 has a first damper input side 95 and a first damper output side 100.
• the second damper unit 75 has a second damper input side 105 and a second damper output side 110.
• the first damper element 85 connects the first damper input side 95 with the first damper output side 100.
• the first damper input side 95 can rotate relative to the first damper output side 100 about an axis of rotation 15 (shown in FIG. 2) and the first damper element 85 in the circumferential direction, for example compress.
• the coupling unit 80 is disposed between the first damper output side 100 and the second damper input side 105 and preferably rigidly connects the first damper output side 100 to the second damper input side 105.
• the second damper element 90 connects the second damper input side 105 to the second damper output side 1 10 in a torque-locking manner. In this case, for torque transmission, the second damper input side 105 relative to the second damper output side 1 10 about the rotation axis 15 (shown in Figure 2) rotate and compress the second damper element 90 in the circumferential direction, for example.
• the second damper output side 1 10 is rigidly connected to the output side 25.
• the hydrodynamic converter 35 has an impeller 1 15 and a turbine wheel 120 and a converter fluid, not shown.
• the impeller 1 15 is coupled by means of hydrodynamic effects during operation of the torque transmission device 10 with the turbine wheel 120, wherein a rotational speed between the impeller 1 15th and the turbine wheel 120 is different.
• the impeller 1 15 is connected to the input side 20 torque-locking.
• the lockup clutch 40 is disposed in parallel with the hydrodynamic converter 35, with a clutch input side 125 of the lockup clutch 40 connected to the input side 20 and a clutch output side 130 of the lockup clutch 40 connected to the first damper input side 95.
• the first speed-adaptive damper 50 is attached to the coupling unit 80. Furthermore, the coupling unit 80 is connected to the turbine wheel 120 torque-locking. On the turbine wheel 120, a second speed-adaptive absorber 55 is further arranged. A third speed-adaptive damper 60 is disposed on the first damper output side 100, and a fourth speed-adaptive damper 65 is disposed on the second damper input side 105.
• the torque to be transmitted has a rotational irregularity, for example a torsional vibration
• the rotational nonuniformity is reduced by a resilient movement of the damping elements 85, 90.
• the speed-adaptive absorbers 50, 55, 60, 65 are excited and at least partially cancel the rotational synchronous shape, so that a particularly smooth torque is provided on the output side 25.
• FIG. 2 shows a half-longitudinal section through the torque transmission device 10 shown schematically in FIG. 1, wherein the illustration of the impeller 15 has been dispensed with.
• the lock-up clutch 40 is exemplified in the embodiment as a multi-plate clutch.
• the coupling output side 130 is connected to a first damper input side 135 forming the first damper input side 95.
• the first damper input side 95 has a first damper input part 135.
• the first damper input part 135 is connected radially inwardly with the clutch output side 130. Radially on the outside, the first damper input part 135 is coupled to a first end side of the first damper element 85.
• the first damper output side 100 includes a first damper output part 145 and a second damper output part 150.
• the first damper output part 145 and the second damper output part 150 are axially spaced from each other with the first damper input part 135 axially engaged between the first damper output part 145 and the second damper output part 150.
• the first damper output part 145 and the second damper output part 150 are connected to each other, for example, riveted together, screwed or glued.
• the first damper output side 100 is coupled to a second end side of the first damper element 85. Further, the first damper output side 100 defines, by way of example, a position of the first damper element 85.
• the output side 25 has, for example, an output shaft 155, wherein the output shaft 155 can also be designed as a transmission input shaft of the transmission device 30.
• the output shaft 155 has a first portion 160 and a second portion 165, which in the embodiment is arranged, for example, axially adjacent to the first portion 160.
• the second section 165 on the circumference has a first external toothing 166, while, for example, the circumference of the first section 160 has a sliding surface on the outside.
• the coupling unit 80 has a first coupling part 170, at least one second coupling part 175 and a connecting hub 176.
• the first coupling part 170 and / or the second coupling part 175 is disc-shaped and connected radially on the outside to the second damper output part 150. It is conceivable that the first coupling part 170 and the second damper output part 150 are formed in one piece and of the same material.
• the first coupling part 170 has a first internal toothing 180 and the second coupling part 175 has a second internal toothing 185.
• the first internal toothing 180 and the second internal toothing 185 are designed identically by way of example.
• the connecting hub 176 is disposed radially inwardly rotatable on the first portion 160 of the output shaft 155.
• the connecting hub 176 has a second outer toothing 190, wherein the second outer toothing 190 is formed corresponding to the first inner toothing 180 and the second inner toothing 185.
• the connecting hub 176 couples the first coupling part 170 with the second coupling part 175.
• means not shown may be provided to define an axial position of both the connecting hub 176 and the first and / or the second coupling part 170, 175.
• the first damper unit 70 is disposed axially adjacent to the lock-up clutch 40.
• the second damper unit 75 is disposed axially between the turbine wheel 120 and the first damper unit 70.
• the second damper input side 105 has a second damper input part 195 and a third damper input part 200 spaced apart axially from the second damper input part 195.
• the second and third damper input parts 195, 200 are connected to each other.
• the third damper input part 200 is arranged on a side facing away from the first damper unit 70 side and radially inwardly connected to the turbine wheel 120.
• Radially on the outside, the second coupling part 175 is connected to the second damper input part 195.
• the second coupling part 175 and the second damper input part 195 are formed integrally and of the same material.
• the second damper input part 195 and the second coupling part 175 may also be formed in several parts, wherein in this embodiment with respect to the embodiment shown in Figure 2, the second damper input part 195 is connected radially inwardly on a radially outer side of the second coupling member 175.
• the second and third damper input parts 195, 200 are coupled to a first end side of the second damper element 90.
• the second damper output side 110 has a third damper output part 205.
• the third damper output part 205 is coupled radially on the outside to a second end side of the second damper element 90. Radial on the inside, the third damper output part 205 has a third internal toothing 210, which is designed corresponding to the first external toothing 166 of the output shaft 155 and engages in the first outer toothing 166.
• the first speed-adaptive damper 50 has a first damper flange 215 and a first damper mass 220.
• the first speed-adaptive damper 50 is formed as an external centrifugal pendulum, so that the first damper mass 220 is disposed on both sides of the first damper flange 215.
• the first speed-adaptive damper 50 comprises a guide device (not shown), with which the first damper mass 220 is coupled to the first Tilgerflansch 215, wherein upon initiation of the rotational nonuniformity in the first Tilgerflansch 215, the first Tilgermasse 220 along a first Tilgerbahn is guided by the first guide means.
• the first damper flange 215 is arranged axially between the first and second coupling parts 170, 175 and the damper units 70, 75.
• the fourth internal toothing 225 is formed corresponding to the second external toothing 190 and engages in the second external toothing 190 of the connecting hub 176, so that the first Tilgerflansch 215 torque-locking manner with the connecting hub 176 and thus also with the first coupling part 170 and the second coupling part 185 is coupled.
• the first damper mass 220 is arranged radially outside the first damper unit 70 and the second damper unit 75.
• the second speed-adaptive damper 55 has a second damper flange 230 and a second damper mass 235, wherein the second damper mass 235 is coupled to the second damper flange 230 by a second guide device (not shown) and by the second guide device when initiation of rotational irregularities in the second Tilgerflansch 230 along a second Tilgerbahn is performed to cancel the rotational nonuniformity.
• Radially inside the second Tilgerflansch 230 is connected to the turbine 120. In this case, axially the second Tilgerflansch 230 between the turbine 120 and the second damper unit 75 is arranged.
• the third speed-adaptive absorber 60 is arranged axially on a side facing the lock-up clutch 40 and axially overlapping to the first damper unit 70.
• the third speed-adaptive damper 60 is disposed radially outward of the first damper unit 70, and is similar to the first speed-adaptive damper 50 and has a third Tilgerflansch 240 and a third damper mass 245, by means of a third guide means, not shown, with the third Tilgerflansch 240th is coupled and when introducing rotational irregularities in the third Til gerflansch 240 along a third Tilgerbahn leads.
• the third Tilgerflansch 240 is in the embodiment, for example, radially inwardly connected to the second damper output member 150.
• the second damper output part 150, the first coupling part 170 and the third damper flange 240 are integral and have the same material and, for example, disc-shaped. Of course, another embodiment is also conceivable.
• the fourth speed-adaptive absorber 65 is arranged axially between the first and second speed-adaptive absorbers 50, 55 and radially outside the row damper 45 and has a fourth absorber flange 250 and a fourth absorber mass 255.
• the fourth damper mass 255 is coupled to the fourth damper flange 250 by means of a fourth guide device (not illustrated).
• a fourth guide device not illustrated.
• the fourth Tilgerflansch 250 is in the embodiment radially inwardly connected to the second damper input part 195.
• the second coupling part 175, the second damper input part 195 and the fourth damper flange 250 are embodied in one piece and in the same material, for example disc-shaped as shown in FIG.
• all the speed-adaptive absorbers 50, 55, 60, 65 are arranged radially outside relative to the first damper unit 70 and the second damper unit 75 and at the same radial height.
• another arrangement of the speed-adaptive damper 50, 55, 60, 65 is conceivable.
• the first damper element 85 When the torque is introduced from the input side 20 to the output side 25, the first damper element 85 is clamped in the circumferential direction by the first damper input part 135 and the first and second damper output parts 145, 150, thus transmitting the torque between the first damper input side 95 and the first damper output side 100 , The torque is then transmitted from the second damper output part 150 to the first coupling part 170, which in turn transmits the torque via the first internal toothing 180 into the connection. hub 176 initiates. The rotational irregularities are also conducted via the connecting hub 176 to the first Tilgerflansch 215, which is not in the direct torque flow. The torque is introduced past the first Tilgerflansch 215 in the second coupling part 175.
• the second coupling part 175 transmits the torque further into the second damper input part 195 which, together with the third damper input part 200, braces the second damper element 90 in the circumferential direction. Due to the tension, the second damper element 90 transfers the torque to the third damper output part 205, which in turn initiates the torque via the third internal toothing 210 into the output shaft 155.
• FIG. 3 shows a semi-longitudinal section through a torque transmission device 10 according to a second embodiment.
• the torque transmission device 10 is substantially identical to the torque transmission device 10 shown in FIGS. 1 and 2.
• the coupling unit 80 additionally has a third coupling part 260 and a fourth coupling part 265.
• the third coupling part 260 has a fifth internal toothing 270, which corresponds to the second External teeth 190 of the connecting hub 176 is formed.
• the fifth internal toothing 270 engages in the second external toothing 190, so that the third coupling part 260 is connected in a torque-locking manner to the connection hub 176.
• the third coupling part 260 is arranged axially between the first Tilgerflansch 215 and the second damper input part 195 and formed disc-shaped.
• the third coupling part 260 is connected to the fourth coupling part 265 by a first connector 280.
• the first connector 280 is detachable by an axial movement, so that the fourth coupling part 265 can be easily separated from the third coupling part 260 in an axial insertion movement and reassembled.
• the fourth coupling part 265 may have finger sections extending in the axial direction, which engage radially outward on the third coupling part 260 in respectively corresponding receptacles and thus connect the third coupling part 260 to the fourth coupling part 265 in a torque-locking manner.
• the third coupling part 260 is, for example, disc-shaped, whereas the fourth coupling part 265 extends substantially in the axial direction and may be, for example, annular. Furthermore, the fourth coupling part 265 is arranged radially outside the second damper unit 75 and radially inward to the speed-adaptive absorbers 50, 55, 60, 65. The fourth coupling part 265 is connected to the turbine wheel 120 axially at the rear in relation to the first connector 280. In addition, in the embodiment, the fourth coupling part 265 is additionally connected to the fourth damper flange 250 of the fourth speed-adaptive damper 65 by means of a second plug connection 285. The second connector 285 is formed so that it is connectable or detachable in the axial direction.
• the second connector 285 may be formed by tabs of the fourth coupling part 265, which extend in sections in the axial direction and engage in recesses provided correspondingly in the fourth Tilgerflansch 250.
• FIG. 4 shows a semi-longitudinal section through a torque transmission device 10 according to a third embodiment.
• the torque transmission device 10 is formed substantially identical to the embodiment shown in Figure 3.
• the second speed-adaptive absorber 55 is connected to the turbine wheel 120 by means of a third plug connection 290, which can be connected or released in the axial direction.
• the third connector 290 may be substantially identical to the first and second connectors 280, 285 illustrated in FIG.
• the torque transmitting device 10 comprises a first clamping means 295 and a second clamping means 300.
• the first clamping means 295 is arranged in the circumferential direction between the first coupling part 170 and the first Tilgerflansch 215 and braces the first Tilgerflansch 215 relative to the first coupling part 170 in the circumferential direction. This ensures that a gearing rattling during engagement of the first inner toothing 180 and the fourth inner toothing 225 on the second outer toothing 190 is avoided.
• the second clamping means 300 braces the third coupling part 260 with respect to the first Tilgerflansch 215.
• the second example
• FIG. 5 shows a half longitudinal section through a torque transmission device 10 according to a fourth embodiment.
• the torque transmission device 10 is essentially identical to the embodiment shown in FIGS. 1 to 4, in particular to the embodiment shown in FIG. 4.
• the second clamping means 300 shown in FIG. 4 is dispensed with.
• the coupling unit 80 has a support element 305, which has a seventh internal toothing 310, which engages in the second external toothing 190.
• the support element 305 extends in the radial direction and is substantially disc-shaped.
• the first clamping means 295 is arranged between the support element 305 and the first coupling part 170 and clamps the first coupling part 170 relative to the support element 305 in the circumferential direction.
• the support element 305 is arranged in the axial direction furthest outward on the side of the connection hub 176 facing the lockup clutch 40.
• FIG. 6 shows a semi-longitudinal section through a torque transmission device 10 according to a fifth embodiment.
• the torque transmission device 10 is essentially a combination of the embodiment shown in FIG. 2 and the embodiment of the torque transmission device 10 shown in FIGS. 4 and 5. Deviating from this, the second plug connection 285 and the third coupling part 260 are dispensed with.
• the fourth coupling part 265 is connected to the third damper output part 205 by means of the first connector 280.
• the first connector 280 is arranged radially outside the second damper unit 75.
• the turbine wheel 120 is rotatably mounted on the output shaft 155 by means of a turbine flange 311.
• the turbine flange 311 is arranged radially on the inside of the turbine wheel 120.
• FIG. 7 shows a half-longitudinal section through a torque transmission device 10 according to a sixth embodiment.
• the torque transmission device 10 is essentially identical to the torque transmission device 10 shown in FIG.
• the first connector 280 is arranged between the fourth coupling part 265 and the second damper input part 195. formed, so that the fourth coupling part 265 radially outwardly to the second
• Damper element 90 engages the second damper input part 195.
• the engagement of the fourth coupling part 265 in the fourth Tilgerflansch 250 can take place.
• FIG. 8 shows a semi-longitudinal section through a torque transmission device 10 according to a seventh embodiment.
• the torque transmission device 10 is essentially identical to the torque transmission device 10 explained in FIG. Deviating from this, the torque transmission device 10 has a fifth speed-adaptive absorber 315.
• the fifth speed-adaptive damper 315 has a fifth damper flange 320 and at least a fifth damper mass 325.
• the fifth absorber mass 325 is connected to the fifth absorber flange 320 by means of a fifth guide device (not shown). Upon initiation of rotational irregularities in the fifth damper flange 320, the fifth damper mass 325 is passed through the fifth guide along a fifth damper track.
• the fifth absorber mass 325 at least partially eliminates the rotational nonuniformity.
• the fifth Tilgerflansch 320 extends in the radial direction and is radially inwardly connected to the fourth Kopel pelteil 265.
• the fifth speed-adaptive damper 315 is arranged between the second damper unit 75 and the first to fourth speed-adaptive damper 50, 55, 60, 65 in the radial direction.
• the fifth speed-adaptive damper 315 is arranged between the turbine wheel 120 and the fourth damper flange 250.
• FIG. 9 shows a semi-longitudinal section through a torque transmission device 10 according to an eighth embodiment.
• the torque transmission device 10 is essentially a combination of the torque transmission devices 10 explained in FIGS. 2 and 6.
• the connecting hub 176 is dispensed with.
• the first section 160 of the output shaft 155 can be dispensed with.
• the second section 165 adjoins the output shaft 155 directly to a region on which the turbine wheel 120 is rotatably mounted on the output shaft 155 rotatable relative to the output shaft 155.
• first coupling part 170 and the second coupling part 175 is shortened inwards in the radial direction, so that radially inwardly the first coupling part 170 and the second coupling part 175 are arranged at a distance from the output shaft 155.
• first clamping means 295 is provided, wherein the first clamping means 295 braces the first coupling part 170 relative to the second coupling part 175.
• fourth Tilgerflansch 250 engage in the first clamping means 295.
• the first damper element 85 has a first rigidity.
• Damper element 90 has a second rigidity.
• the first tensioning means 295 has a third rigidity, wherein the third rigidity is greater than the first rigidity and / or the second rigidity. It is particularly advantageous if the third rigidity is at least twice, preferably five times, the first rigidity and / or the second rigidity. However, the third stiffness should be at least less than one hundred times the first stiffness and / or the second stiffness.
• FIG. 10 shows a semi-longitudinal section through a torque transmission device 10 according to a ninth embodiment.
• the torque transmission device 10 is designed substantially identical to the torque transmission device 10 shown in FIG. Deviating from this, the first speed-adaptive absorber 50 is dispensed with.
• the first clamping means 295 comprises a plate spring or a leaf spring, which in the circumferential direction connects the first coupling part 170 to the second coupling part 175 in a torsionally strong manner in a particularly rigid manner.
• Figure 1 1 shows a semi-longitudinal section through a torque transmission device 10 according to a tenth embodiment.
• the torque transmitting device 10 is essentially a combination of the torque transmission devices 10 shown in FIGS. 9 and 10.
• the first tensioning device 295 is designed as a bow spring or pressure spring as explained in FIG. 9 and clamps the first coupling part 170 with the second coupling part 175 in the circumferential direction and has the figure 9 and 10 explained third stiffness.
• FIG. 12 shows a semi-longitudinal section through a torque transmission device 10 according to an eleventh embodiment.
• the torque transmission device 10 is designed substantially identical to the embodiments shown in FIGS. 9 to 11.
• the second coupling part 175 is dispensed with.
• the first coupling part 170 is arc-shaped relative to the half-longitudinal section shown in FIG. 11. At one end of the first coupling part 170, which is arranged on a side facing away from the second damper output part 150, the first coupling part 170 by means of the second connector 285 with the second damper input part 195 and the fourth Tilgerflansch 250 torque-connected.
• the first coupling part 170 engages in the fourth Tilgerflansch 250 or the second damper input part 195 at the free end, so that the mounting direction and / or the dismounting direction of the torque transmission device 10 is ensured in the axial direction.
• FIG. 13 shows a semi-longitudinal section through a torque transmission device 10 according to a twelfth embodiment.
• the torque transmission device 10 is essentially identical to the torque transmission device 10 explained in FIG. Deviating from this, the second plug connection 285 is arranged radially inward to the second damper unit 75.
• the first coupling part 170 can be made longer in the axial direction and with a smaller curvature than in FIG.
• FIG. 14 shows a semi-longitudinal section through a torque transmission device 10 according to a thirteenth embodiment.
• the torque transmission device 10 is essentially identical to the torque transmission device 10 explained in FIG. Deviating from this, the first speed-dependent speed-adaptive absorber 50 is dispensed with.
• the first damper unit 70 has the first damper input part 135 and the second damper input part 195, the first damper output part 145 being arranged axially between the first damper input part 135 and the second damper input part 195.
• the first damper input part 135 and the second damper input part 195 are connected to each other.
• the first coupling part 170 is connected to the third damper input part 200 or to the fourth damper flange 250 by means of the second plug connection 285.
• the first coupling part 170 on the left side that is, on one of the lock-up clutch 40 side facing, in the fourth Tilgerflansch 250 and / or the third Dämpfereingangsteil 200 inserted.
• the second damper unit 75 has the second damper output part 150 and the third damper output part 205, wherein the second damper output part 150 and the third damper output part 205 are connected to each other, in the axial direction between the second damper output part 150 and the third damper output part 205, the third damper input part 200 engages. On the inside, both the second damper output part 150 and the third damper output part 205 engage in the first outer teeth 166 of the output shaft 155 to initiate the torque in the output shaft 155.
• the turbine wheel 120 is connected by means of the second plug connection 285 to the fourth Til- gerflansch 250 and / or the third Dämpfereingangsteil 200 torque-locking.
• the engagement of the fourth coupling part 265 takes place on a side of the fourth Tilgerflanschs 250 facing away from the first coupling part 170 and thus on a side facing the turbine wheel 120 or on a side facing away from the lock-up clutch 40.
• FIG. 15 shows a semi-longitudinal section through a torque transmission device 10 according to a fourteenth embodiment.
• the torque transmission device 10 is designed substantially identical to the embodiment of the torque transmission device 10 explained in FIG. Deviating from this, the connectors 280, 285, 290 are dispensed with.
• the fourth coupling part 265 is designed to be longer in the axial direction than shown in FIG. In this case, the fourth Tilgerflansch 250 and radially inside the third damper input part 200 is attached to the fourth coupling part 265 radially on the outside.
• the first coupling part 170 extends radially outward from the first
• Damper unit 70 radially inward and is connected to the fourth coupling part 265. Further, the fourth speed-adaptive damper 65 is disposed radially between the first damper unit 70 and the second damper unit 75.
• FIG. 16 shows a torque transmission device 10 according to a fifteenth embodiment.
• the torque transmission device 10 is essentially identical to the embodiment of the torque transmission device 10 shown in FIG. 15. Deviating from this, however, the embodiment of the torque transmission device 10 shown in FIG. 16 is narrower in the axial direction than the torque transmission device 10 shown in FIG.
• FIG. 17 shows a semi-longitudinal section through a torque transmission device 10 according to a sixteenth embodiment.
• the torque transmission device 10 is essentially a combination of the embodiment of the torque transmission device 10 explained in FIGS. 14 and 15. Deviating from this, the fourth speed-adaptive absorber 65 is dispensed with.
• the first coupling part 170 is disk-shaped and integrally formed with both the second Tilgerflansch 230, the first damper output part 145, which is for example radially inside the second Tilgerflansch 230, and the third Dämpfereingangsteil 200, the radially inner side to the first coupling part 170th is arranged.
• the first coupling part 170 is connected to the fourth coupling part 265 by means of the first plug connection 280 and to the turbine wheel 120 via the fourth coupling part 265.
• FIG. 18 shows a torque transmission device 10 according to a seventeenth embodiment.
• the torque transmission device 10 is essentially a combination of the torque transmission device 10 shown in FIG. 15 and the torque transmission device 10 shown in FIG. 17.
• the embodiment is essentially identical to the embodiment shown in FIG. 15, but the one-piece and material-uniform design of the first coupling part 170, the first damper output part 145 and the third Tilgerflanschs 240 and the third damper input part 200 is integrated into the embodiment shown in Figure 15.
• the second connector 285 and the third connector 290 is omitted.
• the fourth speed-adaptive damper 65 is disposed radially inward of the second speed-adaptive damper 55 and fixed to the turbine wheel 120.
• FIG. 19 shows a torque transmission device 10 according to an eighteenth embodiment.
• the torque transmission device 10 is designed substantially identical to the embodiment shown in FIG.
• the first speed-adaptive absorber 50 is additionally provided, wherein the first Tilgerflansch 215 and the first coupling part 170 coincide. That is, the first damper mass 220 is attached to the first coupling part 170.
• the second speed-adaptive absorber 55 is arranged radially at the level of the fourth speed-adaptive absorber 65.
• the first speed-adaptive damper 50 is arranged radially between the first damper unit 70 and the second damper unit 75.
• the first speed-adaptive damper 50, the third speed-adaptive damper 60, the first and second damper units 70 and 75 are arranged axially overlapping.
• an axial overlap is understood to mean that in the projection of at least two components, in the embodiment by way of example the first and third speed-adaptive absorbers 50, 60 and the first and second damper units 70, 75, into a projection plane in which the rotation axis 15 is arranged , along a plane of rotation to the axis of rotation 15, these overlap in the projection plane.
• FIG. 20 shows a half-longitudinal section through a torque transmission device 10 according to a nineteenth embodiment.
• the torque transmission device 10 is designed substantially identical to the embodiment of the torque transmission device 10 shown in FIG. Deviating from this, the second damper output part 150, the first coupling part 170 and the second damper input part 195 are integrally formed of the same material, wherein the first coupling part 170 extends obliquely to the rotation axis 15, whereas the second damper output part 150 and the second damper input part 195 in different planes of rotation run. Furthermore, the first speed-adaptive damper 50 and the fourth speed-adaptive damper 65 are dispensed with, so that only the torque transmission device 10 has the second speed-adaptive damper 55 and the third speed-adaptive damper 60.
• FIG. 21 shows a semi-longitudinal section through a torque transmission device 10 according to a twentieth embodiment.
• the torque transmission device 10 is substantially identical to that in FIG. 20.
• the fourth speed-adaptive damper 65 is provided, wherein the fourth damper flange 250 is radially inwardly connected to the third damper input part 200.
• the Guide shape of the fourth Tilgerflansch 250 and the third Dämpfereingangsteil 200 are integrally formed of the same material.
• the fourth speed-adaptive absorber 65 is arranged radially inward to the second speed-adaptive absorber 55.
• the second speed-adaptive damper 55 is arranged radially further inward than the third speed-adaptive damper 60.
• the fourth speed-adaptive damper 65 is arranged in the axial direction between the second speed-adaptive damper 55 and the third speed-adaptive damper 60.
• the turbine wheel 120 is connected radially on the inside to the third damper input part 200 (as in FIGS. 9, 10, 11, 12 and 13).
• FIG. 22 shows a semi-longitudinal section through a torque transmission device 10 according to a twenty-first embodiment.
• the torque transmission device 10 is designed substantially identical to the embodiment of the torque transmission device 10 shown in FIG. Deviating from this, the fourth speed-adaptive absorber 65 is dispensed with. Furthermore, the first coupling part 170 is connected to the fourth coupling part 265. As a result, the turbine wheel 120 is connected to the first coupling part 170 via the fourth coupling part 265.
• the arrangement of the connection of the first coupling part 170 with the fourth coupling part 265 essentially corresponds to the embodiment explained in FIG. 17.
• the second connector 285 may be provided as explained in Figure 17. In FIG. 22, however, the second connector is used
• FIG. 23 shows a semi-longitudinal section through a torque transmission device 10 according to a twenty-second embodiment.
• the torque transmission device 10 is designed essentially identical to the configuration explained in FIG. Deviating from the fourth speed-adaptive absorber 65 is provided, wherein the fourth Tilgerflansch 250 radially outwardly to the second Damper unit 75 is arranged and connected to a radially inner end with the third damper input part 200.
• FIGS. 1 to 23 ensures a modular construction of the torque transmission device 10.
• this makes it possible to provide a modular system in which, depending on the respective components to be combined, in particular the first to fourth speed-adaptive absorbers 50, 55, 60, 65 and the damper units 70, 75, these are installed as required or omitted can.
• the first damper unit 70 is constructed independently and thus independently of the second damper unit 75, so that both damper units 70, 75, regardless of whether they are provided in the torque transmission device 10, also function as a single component would.
• the envisaged speed-adaptive absorbers 50, 55, 60, 65, 315 and the turbine wheel 120 are envisaged speed-adaptive absorbers 50, 55, 60, 65, 315 and the turbine wheel 120.
• the turbine wheel 120 By coupling the turbine wheel 120 independently of the other components directly or indirectly, for example via the fourth coupling part 265 with the first coupling part 170 of the series damper 45 and / or the speed-adaptive first to fourth absorbers 50, 55, 60, 65 are mounted in different configurations of the torque transmission device 10.
• the compensation in terms of geometrical design is made via the coupling unit 80.
• the hydrodynamic converter 35 can also be dispensed with.

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• 2017
  • 2017-05-31 DE DE102017111930.2A patent/DE102017111930A1/de not_active Withdrawn
• 2018
  • 2018-05-15 WO PCT/DE2018/100457 patent/WO2018219395A1/de active Application Filing
  • 2018-05-15 JP JP2019560757A patent/JP6877584B2/ja active Active
  • 2018-05-15 EP EP18729027.5A patent/EP3631239A1/de not_active Withdrawn
  • 2018-05-15 KR KR1020197033528A patent/KR102541832B1/ko active IP Right Grant
  • 2018-05-15 CN CN201880027078.9A patent/CN110546399B/zh active Active
  • 2018-05-15 DE DE112018002763.5T patent/DE112018002763A5/de active Pending
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